WO2017162060A1

WO2017162060A1 - Damping device and method for medium/low speed magnetic levitation turnout beam

Info

Publication number: WO2017162060A1
Application number: PCT/CN2017/076412
Authority: WO
Inventors: 靖仕元; 王玉泽; 郭志勇; 章致
Original assignee: 中铁第四勘察设计院集团有限公司
Priority date: 2016-03-22
Filing date: 2017-03-13
Publication date: 2017-09-28
Also published as: CN105839513B; CN105839513A

Abstract

Disclosed are a damping and noise reduction device for a medium/low speed magnetic levitation turnout beam. The damping and noise reduction device comprises a pre-embedded board arranged on a bottom flange of the turnout beam and multiple tuning mass dampers installed on the pre-embedded board. Each of the tuning mass dampers comprises a main vibration system having arranged thereon a container provided with a built-in tuning damper. The containers are filled with damping liquid. By adjusting the mass, the rigidity and the damping coefficient parameters of the tuning damping mechanism and by adjusting the size of the containers and the depths of the damping liquid in the containers, the tuning damping mechanism can meet a mass tuning condition and a liquid tuning condition, such that mass tuning and liquid tuning are achieved. Hence damping and noise reduction of the turnout beam are achieved. Further disclosed is a corresponding damping and noise reduction method. On the premise that it is guaranteed that the turnout beam rotates in place within the required time, the vertical vibration acceleration of the turnout beam can be stably reduced to a safe standard with satisfactory leeway of 0.5 g for a long time, and control of the vibration of the turnout beam is achieved.

Description

Medium and low speed magnetic floating raft beam damping device and method

[Technical field]

The invention belongs to the technical field of medium and low speed maglev rail transportation, and particularly relates to a medium and low speed magnetic floating channel truss vibration damping and noise reduction device and method.

[Background technique]

The switch is a line connection device used in rail transit to transfer a rolling stock from one lane to another, usually in a large number of stations and marshalling stations. The track of medium and low speed maglev rail transportation usually includes ballast beam, truss beam, trolley, beam upper rail, driving device, locking device, movable end rail, and electric control system. When the lane change is needed, it is connected from the switch electrical control system. According to the conversion command, the switch drive device drives the switch beam to move laterally, and drives the driven beam to move along the trolley, so that the ballast beam and the guide rail are rotated until the designated truss beam is aligned, and the locking device is locked, thereby realizing the lane change.

When the maglev train passes through the ballast, in order to make the turnout time short, the design of the ballast beam generally adopts the light chemical steel and the diaphragm structure. The natural vibration frequency of the ballast beam is 10-18Hz, and the difference of the natural frequency of each step is small, the magnetic float The self-vibration frequency of the train is close to the natural vibration frequency of the ballast beam, which generates resonance. On the one hand, the resonance will affect the service life of the ballast structure. On the other hand, the vibration is too large, which affects the operation and comfort of the maglev, and generates noise and affects the environment. Therefore, the resonance between the maglev train and the ballast must be treated to reduce and improve the resonance phenomenon between the ballast and the maglev train.

At present, the industry solves the resonance problem mainly by changing the mass of the ballast to change the vibration characteristics. For example, adding a suitable sand (cobblestone) bag (box) processing device to the active beam steel box beam, the solution can improve the vibration characteristics, but the vibration damping effect and the continuous vibration reduction There are still some shortcomings in the stability and other aspects, mainly reflected in the following two aspects:

1) It is difficult to achieve the expected vibration reduction target

The medium and low speed ballast beam design adopts light chemical steel and cross baffle structure. The weight of the ballast beam is about 247KN, which can meet the rotation of the 11KW motor within 15s, and increase the sand (cobblestone) bag (box) in the two beams of the active beam. The quality of the ballast changes the vibration characteristics. The quality of the sand (cobblestone) bag (box) should not be too large (not more than 4000kg). Otherwise, the time requirement of the ballast rotation within 15 seconds cannot be met, and the quality of the belt (box) within the 4000kg has a certain vibration reduction. As a result, the vertical vibration acceleration can be reduced from 3.3 g to about 1.0 g to about 1.3 g, but it is difficult to achieve vertical vibration acceleration control within a safe and comfortable standard of no more than 0.5 g.

2) unstable vibration damping effect

The sand (cobblestone) bag (box) changes the vibration characteristics in the two beams of the active beam. As the maglev train runs multiple times, its damping effect is getting worse and worse, mainly because the sand (pebble) is loose when it starts to drive. It has a certain damping effect. As the train vibrates several times, the sand (cobblestone) becomes denser, and its damping effect becomes smaller and smaller. Finally, only the mass acts, the damping effect becomes worse and worse, and its vibration damping stability is poor.

[Summary of the Invention]

In view of the above defects or improvement requirements of the prior art, the present invention provides a vibration damping and noise reduction device and method for a medium and low speed magnetic floating raft beam, which are provided by setting a plurality of sets of tuned mass dampers in a steel box ballast beam. The vibration energy of the ballast beam is transferred to the vibration of the moving mass in the tuned mass damper, and the safety and comfort standard of the vertical vibration acceleration of the ballast beam can be reduced to 0.5g for a long time under the premise of ensuring that the ballast beam is rotated in the specified time. Inside, the control of the vibration of the ballast beam is realized.

In order to achieve the above object, according to an aspect of the present invention, a vibration damping and noise reduction apparatus for a medium and low speed magnetic floating raft beam is provided, characterized in that the apparatus comprises:

a pre-embedded plate disposed on the bottom flange of the ballast beam;

a plurality of tuned mass dampers fixedly mounted on the embedded plate;

Wherein, the tuned mass damper comprises a main vibration system, and the main vibration system is provided with a container with a built-in tuned damper, the container is filled with a damping fluid, and the quality and rigidity of the tuned damping mechanism are adjusted And the damping coefficient, and adjusting the size of the container and the depth of the damping fluid therein to satisfy the mass tuning and liquid tuning conditions, respectively, in such a manner that the vibration energy energy of the ballast beam is transferred to the vibration of the moving mass and passes The damping fluid dissipates the vibration energy of the active mass to achieve mass tuning and liquid tuning, thereby achieving vibration and noise reduction of the ballast beam.

As a further preferred embodiment of the present invention, the tuned mass dampers are four or more.

As a further preferred embodiment of the invention, each set of said tuned mass dampers are symmetrically distributed on the ballast beam.

As a further preferred embodiment of the invention, each set of tuned mass dampers includes three to six mass dampers that are evenly disposed laterally along the ballast beam.

As a further preferred embodiment of the invention, each set of said tuned mass dampers has a damping ratio of 0.1 and a frequency preferably in the range of 16.56-17.56.

As a further preferred embodiment of the invention, each set of said tuned mass dampers has a mass of 45-55 kg.

In the present invention, the medium and low speed ballast beam tuned mass damper system (TMD, Tuned Mass Damper) transfers the vibration energy of the ballast beam to the vibration of the moving mass in the TMD within the tuning range by adjusting its own frequency, within the TMD. The damping device will fully dissipate the vibration energy of the moving mass to achieve the purpose of controlling the vibration of the ballast beam.

The invention can greatly reduce the vibration response by installing a plurality of sets of TMD tuned mass dampers in the active beam to increase the damping value.

According to another aspect of the present invention, a vibration damping and noise reduction method for a medium and low speed magnetic floating raft beam is provided, the method comprising:

Providing a pre-embedded plate on the bottom flange of the ballast beam;

Fixing a plurality of tuned mass dampers on the embedded plate, wherein the tuned mass damper comprises a main vibration system, the main vibration system is provided with a container with a built-in tuned damper, and the container is filled with a damping fluid ;

Adjusting the mass, stiffness and damping coefficient parameters of the tuned damping mechanism, and adjusting the size of the container and the depth of the damping fluid therein to satisfy the mass tuning and liquid tuning conditions, respectively, so that the vibration energy of the ballast beam can be transferred to the activity The vibration of the mass, the damping fluid dissipates the vibration energy of the active mass, achieves mass tuning and liquid tuning, and thus achieves vibration and noise reduction of the ballast beam.

In general, the above technical solutions conceived by the present invention have the following beneficial effects compared with the prior art:

(1) In the present invention, a damping mass is further disposed in the main vibration system, and at the same time, the mass is placed in the damping fluid, and the damping fluid is pushed during the movement of the mass by adjusting the frequency of the mass and the damping parameter of the damping fluid. By double-tuning the mass and the liquid, and simultaneously utilizing the coupling effect of the fluid and the solid, in the case of greatly reducing the volume of the vibration damping device, not only the parameter adjustment of the entire vibration damping device is more convenient, but also the vibration damping effect is further improved. good;

(2) In the present invention, after the damper is installed, the mass of the ballast is only increased by 1200 kg, which satisfies the requirement of 15 s rotation time, the vertical vibration acceleration of the ballast beam is reduced to 0.5 g safety and comfort standard, and the vibration damping is stable for a long time.

[Description of the Drawings]

Figure 1 is a schematic view showing the principle of the vibration damping device of the present invention;

2 is a schematic view showing a TMD and a 1-span active beam mounting structure in a vibration damping device according to an embodiment of the present invention;

Figure 3 (a) is a schematic view of the structure of the TMD and the 1 span of the active beam installed in the damping device of Figure 2; 3 (b) is a schematic view of the planar structure of the TMD and 1 span of the active beam; 3 (c) is TMD Installation with 1 span active beam Schematic diagram of the side structure.

[detailed description]

The present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It is understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention. Further, the technical features involved in the various embodiments of the present invention described below may be combined with each other as long as they do not constitute a conflict with each other.

The structure of the vibration damping device according to a preferred embodiment of the present invention is as shown in FIGS. 1 and 2. The vibration damping device of the embodiment includes a plurality of sets of tuned mass dampers, and a certain thickness is welded on the bottom flange of the I-beam on both sides of the ballast beam ( For example, a pre-buried plate of 24 mm), the bottom of the tuned mass damper is bolted to the embedded plate.

In one embodiment, the entire set of ballast active beams are two spans, preferably four sets per damper, each set of dampers preferably comprising three dampers arranged side by side, preferably evenly spaced transversely along the ballast beam. Of course, the number of groups of dampers in the present invention is not limited thereto, and may be selected by modal analysis according to specific conditions.

Due to the sensitivity of the TMD damper to the frequency, the controllable frequency range is narrow for a single frequency TMD. Once the frequency of the main structure deviates from the controllable frequency range, the control effect is greatly reduced. For the vibration reduction project of the maglev beam of the maglev engineering, the quality of the ballast beam is light, and the frequency of the ballast beam will be affected when the train passes, and the passengers will have different degrees of influence. Therefore, the actual frequency of the ballast beam during the operation period It is not fixed, so it is controlled by multiple tuned mass liquid double tuned dampers (TLMD).

In fact, the medium and low speed ballast beam control vibration has the following two characteristics: 1) The controlled frequency is up to 18 Hz. The main vibration frequency of the ballast beam state is 18 Hz. At this frequency, the vibration attenuation duration of the ballast beam is very short after the following car leaves. Therefore, the TMD mainly controls the vehicle state (ie, the controlled frequency is 18 Hz); 2) the ballast beam The no-load frequency differs greatly from the vehicle frequency, and the vehicle frequency varies with the mass of the vehicle body. Therefore, multiple sets of frequency distributed MTMD dampers are used for vibration control.

The working principle of the damper is shown in Fig. 1. On the main vibration system with mass M, stiffness K and damping coefficient C, a container with built-in mass tuned damper is set. The mass of the mass tuned damper in the container is m, and the stiffness is k, the damping coefficient is c, adjust the mass m, stiffness k, damping coefficient c and other parameters of the mass damping mechanism to meet the quality tuning conditions to achieve the quality tuning damping effect. At the same time, the damping liquid is filled in the container, and the size of the container and the depth of the damping liquid therein are adjusted to satisfy the liquid tuning condition to achieve the vibration damping effect of the liquid tuning. As the mass m moves to move the damping fluid, it has a larger amplitude, which is more conducive to its absorption and dissipation of the energy of the main vibration system, that is, through the double tuning of mass and liquid, while utilizing the coupling of fluid and solid, When the volume of the vibration damping device is reduced, not only the parameter adjustment of the entire vibration damping device is more convenient, but also the vibration damping effect is better.

In Figure 1, the damper dynamics equation is:

In the formula:

M, C, K - the mass coefficient, damping coefficient and stiffness coefficient of the main structure; p(t) - the external excitation of the main structure; y - the displacement of the main structure;

- the mass coefficient, damping coefficient and stiffness factor of the i-th TMD;

- the displacement of the i-th TMD;

- The displacement of the i-th TMD at the junction with the main structure.

The vibration mode decomposition of the above vibration system is carried out to obtain its modal equation:

Where: q _k - the kth order displacement of the main structure; γ _{k -} the relative displacement of the TLMD to the kth order mode of the structure; m _k , ω _k , ζ _k , F _k - the modal mass of the kth order of the main structure, Circular frequency, modal damping and modal external force;

- the mass ratio of the i-th TLMD to the kth-order mode of the main structure, the circular frequency, the damping ratio, and the mode shape value of the main structure at the mounting position.

The goal of the multi-objective satisfaction control theory is that when the mass ratio of multiple TMDs is constant, the power magnifications of the main structure (the ballast beam) and the TMD take the minimum value.

In one embodiment, the optimization parameters for setting up four sets of TMDs by optimization are shown in the following table.

Under this parameter, the maximum power amplification factor of the active beam is 6.37.

After the TMD beam is installed, the vertical vibration acceleration is reduced from 3.3g without the TMD to 0.5g safety and comfort standard, and it can be stable for a long time. After installing the damper, the ballast quality is only increased by 1200kg, meeting the 15s rotation time requirement.

In addition, the damping fluid in the damper provides a stable and easy-to-adjust damping for the entire damping device, and also provides an anti-corrosion environment for the components of the damping device, prolonging the service life of the entire damping device and reducing the total life of the device. overall costs.

Those skilled in the art will appreciate that the above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and scope of the present invention, All should be included in the scope of protection of the present invention.

Claims

A vibration and noise reduction device for a medium and low speed magnetic floating raft beam, characterized in that the device comprises:

a pre-embedded plate disposed on the bottom flange of the ballast beam;

a plurality of tuned mass dampers fixedly mounted on the embedded plate;

Wherein the tuned mass damper comprises a main vibration system, the main vibration system is provided with a container with a built-in tuned damper, the container is filled with a damping fluid, by adjusting the quality, stiffness and damping coefficient of the tuned damping mechanism, and Adjusting the size of the container and the depth of the damping fluid therein to satisfy the mass tuning and liquid tuning conditions, respectively, in such a manner that the vibration energy energy of the ballast beam is transferred to the vibration of the movable mass and is dissipated through the damping fluid The vibration energy of the mass reaches the mass tuning and liquid tuning, which in turn achieves vibration and noise reduction of the ballast beam.
The vibration damping and noise reduction device for a medium-low speed magnetic floating truss beam according to claim 1, wherein the tuned mass dampers are four or more.
The vibration damping and noise reduction apparatus for a medium-low speed magnetic floating truss beam according to claim 1 or 2, wherein each of said sets of said tuned mass dampers is symmetrically distributed on the ballast beam.
A vibration damping and noise reduction apparatus for a medium and low speed magnetic floating raft beam according to claim 3, wherein each of said set of tuned mass dampers comprises three to six mass dampers arranged uniformly in the lateral direction of the ballast beam.
The vibration damping and noise reduction device for a medium-low speed magnetic floating truss beam according to any one of claims 1 to 4, wherein each of said set of tuned mass dampers has a damping ratio of 0.1 and a frequency preferably in the range of 16.56-17.56. Inside.
A vibration damping and noise reduction apparatus for a medium and low speed magnetic floating raft beam according to any one of claims 1 to 4, wherein each of said set of tuned mass dampers has a mass of 45-55 kg.
A vibration and noise reduction method for a medium and low speed magnetic floating raft beam, characterized in that the method comprises:

Providing a pre-embedded plate on the bottom flange of the ballast beam;

Mounting a plurality of tuned mass dampers on the embedded plate, wherein the tuned mass damper package The main vibration system is provided with a container with a built-in tuned damper, and the container is filled with a damping fluid;

Adjusting the mass, stiffness and damping coefficient parameters of the tuned damping mechanism, and adjusting the size of the container and the depth of the damping fluid therein to satisfy the mass tuning and liquid tuning conditions, respectively, so that the vibration energy of the ballast beam can be transferred to the activity The vibration of the mass, the damping fluid dissipates the vibration energy of the active mass, achieves mass tuning and liquid tuning, and thus achieves vibration and noise reduction of the ballast beam.
A vibration damping and noise reduction method for a medium-low speed magnetic floating raft beam according to claim 7, wherein the tuned mass dampers are four or more.
A vibration damping and noise reduction method for a medium and low speed magnetic floating raft beam according to claim 7 or 8, wherein each of said set of tuned mass dampers comprises three to six mass dampers, uniform along the transverse direction of the ballast beam Arrangement.
A vibration damping and noise reduction apparatus for a medium and low speed magnetic floating raft beam according to any one of claims 7-9, wherein each of said set of tuned mass dampers has a damping ratio of 0.1 and a frequency preferably in the range of 16.56-17.56. Inside.